US11339676B2 - Aircraft gas turbine, and rotor blade of aircraft gas turbine - Google Patents

Aircraft gas turbine, and rotor blade of aircraft gas turbine Download PDF

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Publication number
US11339676B2
US11339676B2 US16/761,510 US201816761510A US11339676B2 US 11339676 B2 US11339676 B2 US 11339676B2 US 201816761510 A US201816761510 A US 201816761510A US 11339676 B2 US11339676 B2 US 11339676B2
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Prior art keywords
rotor blade
rotor
turbine
guide member
peripheral surface
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US16/761,510
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US20210180464A1 (en
Inventor
Daigo Fujimura
Takaaki HASE
Hirokazu Hagiwara
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Mitsubishi Heavy Industries Aero Engines Ltd
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Mitsubishi Heavy Industries Aero Engines Ltd
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Assigned to MITSUBISHI HEAVY INDUSTRIES AERO ENGINES, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES AERO ENGINES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FUJIMURA, DAIGO, HAGIWARA, HIROKAZU, Hase, Takaaki
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/22—Blade-to-blade connections, e.g. for damping vibrations
    • F01D5/225—Blade-to-blade connections, e.g. for damping vibrations by shrouding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/28—Arrangement of seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/32—Application in turbines in gas turbines
    • F05D2220/323—Application in turbines in gas turbines for aircraft propulsion, e.g. jet engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/55—Seals
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft

Definitions

  • the present invention relates to an aircraft gas turbine and a rotor blade of an aircraft gas turbine.
  • a part of the main flow of a combustion gas passes through the gap between a rotor blade and a housing without passing through the rotor blade. Accordingly, it is desired to reduce the flow rate of the combustion gas passing through the gap to improve the output.
  • Patent Literature 1 discloses an aircraft gas turbine in which a fin or a honeycomb facing the tip of the fin via a gap is provided as a non-contact seal structure so that the flow rate of the combustion gas passing through the gap between the rotor blade and the housing is reduced.
  • the flow of the combustion gas passing through the gap in the seal structure may flow radially inward from the cavity formed between the rotor blade and a stationary blade.
  • the direction of flow of the combustion gas that has passed through the gap of the seal structure is significantly different from the direction of flow of the main flow that has passed through the rotor blade. Accordingly, the combustion gas that has passed through the gap of the seal structure collides and is mixed with the main flow and an increase in mixing loss may arise as a result.
  • An object of the present invention is to provide an aircraft gas turbine and a rotor blade of an aircraft gas turbine with which it is possible to achieve an improvement in output by reducing the mixing loss at a time when the combustion gas that has passed through the gap of the seal structure collides and is mixed with the main flow that has passed through the rotor blade.
  • an aircraft gas turbine includes a rotor rotating around an axis, a rotor blade having a rotor blade main body extending radially outward from the rotor, a rotor blade shroud provided at a tip of the rotor blade main body, and a fin projecting from an outer peripheral surface of the rotor blade shroud, a casing surrounding the rotor and the rotor blade from an outer periphery side and forming a gap with the fin, a stationary blade having a stationary blade shroud fixed to the casing on a downstream side of the rotor blade and forming a cavity with at least the rotor blade shroud and the fin and a stationary blade main body extending radially inward from the stationary blade shroud, and a guide member provided in the cavity and extending inward from a radial outer side, an inner-side end part of the guide member on a radial inner side facing the outer peripheral surface of the rotor blade
  • a combustion gas that has passed through the gap formed between the casing and the fin flows into the cavity formed by the rotor blade shroud, the fin, and the stationary blade shroud.
  • the combustion gas G passes between the inner-side end part of the guide member and the outer peripheral surface of the rotor blade shroud, which are spaced apart in the radial direction about the axis. Accordingly, the combustion gas G is blown out in an axial direction from the cavity. In other words, it is possible to align the direction of flow of the combustion gas blown out of the cavity with the direction of flow of a main flow.
  • the flow of the combustion gas that has passed through the gap between the casing and the fin and flowed into the cavity can be guided to the radial inner side by the guide member. Accordingly, it is possible to cause the combustion gas to collide with the combustion gas, which is about to flow into the gap between the inner-side end part of the guide member and the outer peripheral surface of the rotor blade shroud, from a direction intersecting with the flow of the combustion gas.
  • the flow of the combustion gas about to flow in between the inner-side end part of the guide member and the outer peripheral surface of the rotor blade shroud can be contracted and the flow rate of the combustion gas merging with the main flow from the cavity can be reduced.
  • the outer peripheral surface of the rotor blade shroud facing the inner-side end part may be formed in parallel with the axis.
  • the guide member according to the first or second aspect may be provided with an inclined portion inclined so as to approach the stationary blade in a direction in which the axis extends radially outward from the inner-side end part.
  • the gap between the inner-side end part and the outer peripheral surface of the rotor blade shroud may be formed so as to be larger than the gap between the fin and the casing.
  • the inner-side end part of the guide member may be disposed closer to the radial inner side than an inner peripheral surface of the stationary blade shroud.
  • a rotor blade of an aircraft gas turbine is a rotor blade of an aircraft gas turbine provided with a rotor rotating around an axis, a casing surrounding the rotor from an outer periphery side, a stationary blade having a stationary blade shroud fixed to the casing and a stationary blade main body extending radially inward from the stationary blade shroud, and a guide member extending inward from a radial outer side and the rotor blade includes a rotor blade main body extending radially outward from the rotor, a rotor blade shroud provided at a tip of the rotor blade main body, and a fin projecting from an outer peripheral surface of the rotor blade shroud, in which the rotor blade shroud and the fin form a cavity with at least the stationary blade shroud on a downstream side of the rotor blade main body and a radial-inner-side end part of the guide member provided in the cavity faces
  • a combustion gas passes through the gap formed between the casing and the fin and flows into the cavity formed by the rotor blade shroud, the fin, the casing, and the stationary blade shroud.
  • the combustion gas G that has flowed into the cavity is blown out after passing between the inner-side end part of the guide member and the outer peripheral surface of the rotor blade shroud formed in parallel with the axis, which are spaced apart in the radial direction about the axis. Accordingly, the combustion gas G is blown out in an axial direction from the cavity. In other words, it is possible to align the direction of flow of the combustion gas blown out of the cavity with the direction of flow of a main flow.
  • FIG. 1 is a configuration diagram illustrating a schematic configuration of an aircraft gas turbine of an embodiment of the present invention.
  • FIG. 2 is a partial cross-sectional view in which the vicinity of an end part of a rotor blade in the embodiment of the present invention is enlarged.
  • FIG. 3 is a partial cross-sectional view corresponding to FIG. 2 in each modification example of the embodiment of the present invention.
  • FIG. 1 is a configuration diagram illustrating a schematic configuration of the aircraft gas turbine of the embodiment of the present invention.
  • an aircraft gas turbine 100 is for obtaining thrust of an aircraft.
  • This gas turbine 100 mainly includes a compressor 1 , a combustion chamber 2 , and a turbine 3 .
  • the compressor 1 generates high-pressure air by compressing air taken in from an intake duct 10 .
  • This compressor 1 includes a compressor rotor 11 and a compressor casing 12 .
  • the compressor casing 12 covers the compressor rotor 11 from an outer periphery side and extends along an axis Am.
  • a plurality of compressor rotor blade stages 13 arranged with a gap therebetween in the axis Am direction are provided on the outer peripheral surface of the compressor rotor 11 .
  • the compressor rotor blade stages 13 respectively include a plurality of compressor rotor blades 14 .
  • the respective compressor rotor blades 14 of the compressor rotor blade stages 13 are arranged on the outer peripheral surface of the compressor rotor 11 with a gap therebetween in the circumferential direction of the axis Am.
  • a plurality of compressor stationary blade stages 15 arranged with a gap therebetween in the axis Am direction are provided on the inner peripheral surface of the compressor casing 12 .
  • the compressor stationary blade stages 15 are disposed alternately with the compressor rotor blade stages 13 in the axis Am direction.
  • the compressor stationary blade stages 15 respectively include a plurality of compressor stationary blades 16 .
  • the respective compressor stationary blades 16 of the compressor stationary blade stages 15 are arranged on the inner peripheral surface of the compressor casing 12 with a gap therebetween in the circumferential direction of the axis Am.
  • the combustion chamber 2 generates a combustion gas G by mixing a fuel F with the high-pressure air generated by the compressor 1 and performing combustion on the mixture.
  • the combustion chamber 2 is provided between the compressor casing 12 and a turbine casing (casing) 22 of the turbine 3 .
  • the combustion gas G generated by the combustion chamber 2 is supplied to the turbine 3 .
  • the turbine 3 is driven by the high-temperature and high-pressure combustion gas G generated in the combustion chamber 2 . More specifically, the turbine 3 expands the high-temperature and high-pressure combustion gas G and converts the heat energy of the combustion gas G into rotational energy.
  • the turbine 3 includes a turbine rotor 21 and the turbine casing 22 .
  • the turbine rotor 21 extends along the axis Am.
  • a plurality of turbine rotor blade stages 23 arranged with a gap therebetween in the axis Am direction are provided on the outer peripheral surface of the turbine rotor 21 .
  • the turbine rotor blade stages 23 respectively include a plurality of turbine rotor blades 24 .
  • the respective turbine rotor blades 24 of the turbine rotor blade stages 23 are arranged on the outer peripheral surface of the turbine rotor 21 with a gap therebetween in the circumferential direction of the axis Am.
  • the turbine casing 22 covers the turbine rotor 21 from an outer periphery side.
  • a plurality of turbine stationary blade stages 25 arranged with a gap therebetween in the axis Am direction are provided on the inner peripheral surface of the turbine casing 22 .
  • the turbine stationary blade stages 25 are disposed alternately with the turbine rotor blade stages 23 in the axis Am direction.
  • the turbine stationary blade stages 25 respectively include a plurality of turbine stationary blades 26 .
  • the respective turbine stationary blades 26 of the turbine stationary blade stages 25 are arranged on the inner peripheral surface of the turbine casing 22 with a gap therebetween in the circumferential direction of the axis Am.
  • the compressor rotor 11 and the turbine rotor 21 are integrally connected in the axis Am direction.
  • the compressor rotor 11 and the turbine rotor 21 constitute a gas turbine rotor 91 .
  • the compressor casing 12 and the turbine casing 22 are integrally connected along the axis Am.
  • the compressor casing 12 and the turbine casing 22 constitute a gas turbine casing 92 .
  • the gas turbine rotor 91 is integrally rotatable around the axis Am in the gas turbine casing 92 .
  • the compressor rotor 11 gas turbine rotor 91
  • the compressor rotor 11 is first driven to rotate by an external driving source. External air is sequentially compressed as the compressor rotor 11 rotates and high-pressure air is generated. This high-pressure air is supplied into the combustion chamber 2 through the compressor casing 12 .
  • the fuel is mixed with the high-pressure air, combustion is performed on the mixture, and the high-temperature and high-pressure combustion gas is generated as a result.
  • the combustion gas is supplied into the turbine 3 through the turbine casing 22 .
  • a rotational driving force is applied to the turbine rotor 21 (gas turbine rotor 91 ) by the combustion gas sequentially colliding with the turbine rotor blade stage 23 and the turbine stationary blade stage 25 .
  • This rotational energy is mainly used for driving the compressor 1 .
  • the combustion gas G that has driven the turbine 3 is increased in flow speed by an exhaust nozzle 4 , becomes a jet generating thrust, and is discharged to the outside from an injection port 27 .
  • a single-shaft turbojet engine has been described as an example of the aircraft gas turbine in this embodiment. However, the present invention is not limited to the single-shaft turbojet engine and any form of aircraft gas turbine is possible.
  • FIG. 2 is a partial cross-sectional view in which the vicinity of an end part of the rotor blade in the embodiment of the present invention is enlarged.
  • the turbine rotor blade 24 of the turbine 3 has a rotor blade main body 41 , a rotor blade shroud 42 , and fins 43 .
  • the rotor blade main body 41 extends radially outward from the turbine rotor 21 .
  • the rotor blade shroud 42 is provided at a tip 41 a of the rotor blade main body 41 . More specifically, the rotor blade shroud 42 is provided at the tip 41 a of the rotor blade main body 41 on the outer side in a radial direction Dr about the axis Am (hereinafter, simply referred to as a radial outer side Dro).
  • the rotor blade shrouds 42 are formed at all the tips 41 a of the turbine rotor blades 24 disposed side by side in a circumferential direction Dc (see FIG. 1 ) about the axis Am. These rotor blade shrouds 42 form an annular shape by the rotor blade shrouds 42 of the turbine rotor blades 24 mutually adjacent in the circumferential direction Dc being disposed so as to be mutually adjacent. It should be noted that the rotor blade shrouds 42 may be integrally formed in the circumferential direction Dc.
  • the rotor blade shroud 42 illustrated in FIG. 2 illustrates a case where the rotor blade shroud 42 is inclined so as to be disposed on the outer side in the radial direction Dr toward the downstream side of a main flow M with respect to the axis Am.
  • the angle of inclination of the rotor blade shroud 42 is an example and the rotor blade shroud 42 may be formed in parallel with the axis Am.
  • the fin 43 projects from an outer peripheral surface 42 a of the rotor blade shroud 42 .
  • the two fins 43 that are exemplified in this embodiment are provided with a gap therebetween in the direction in which the axis Am extends (hereinafter, simply referred to as an axial direction Da). It should be noted that the two fins 43 will be respectively referred to as a fin 43 A and a fin 43 B in the following description.
  • the fin 43 A and the fin 43 B extend so as to block the gap between the turbine rotor blade 24 and the turbine casing 22 outside the turbine rotor blade 24 in the radial direction Dr.
  • the fin 43 A and the fin 43 B are provided for each turbine rotor blade 24 as in the case of the rotor blade shroud 42 and the fins 43 A and 43 B of the turbine rotor blades 24 mutually adjacent in the circumferential direction Dc form a annular shape continuous in the circumferential direction Dc by being disposed so as to be mutually adjacent.
  • Respective tips 43 a of the fins 43 A and 43 B are disposed via a slight clearance C 1 with respect to the inner peripheral surface of the turbine casing 22 (more specifically, inner peripheral surfaces 22 ca and 22 cb of a damper seal 22 c ).
  • These clearances C 1 are formed as small as possible within a range in which the clearances C 1 do not come into contact with the inner peripheral surface of the turbine casing 22 due to thermal deformation, vibration, or the like.
  • the inclination angles of the fins 43 A and 43 B with respect to the outer peripheral surface 42 a are not limited to a right angle although the fins 43 A and 43 B exemplified in this embodiment extend substantially perpendicularly to the outer peripheral surface 42 a of the rotor blade shroud 42 .
  • the number of the fins 43 is not limited to two.
  • the number of the fins 43 may be one or three or more.
  • the turbine casing 22 includes a casing main body (not illustrated), a blade ring (not illustrated), a heat shield ring (not illustrated), a split ring 22 b , and the damper seal 22 c .
  • the casing main body (not illustrated) is formed in a tubular shape surrounding the turbine rotor 21 and turbine rotor blade 24 from an outer periphery side and supports the blade ring (not illustrated) on the inner periphery side thereof.
  • the blade ring (not illustrated) is formed in an annular shape about the axis Am and is disposed on the radial outer side Dro of a plurality of the split rings 22 b and the turbine stationary blades 26 .
  • the heat shield ring (not illustrated) is disposed between the blade ring (not illustrated) and the split ring 22 b and between the blade ring (not illustrated) and the turbine stationary blade 26 in the radial direction Dr.
  • the heat shield ring (not illustrated) interconnects the blade ring (not illustrated) and the split ring 22 b and interconnects the blade ring (not illustrated) and the turbine stationary blade 26 .
  • the damper seal 22 c prevents a part of the main flow M from passing through the gaps respectively formed between the fin 43 A and the turbine casing 22 and between the fin 43 B and the turbine casing 22 .
  • the damper seal 22 c in this embodiment constitutes a non-contact seal structure with the fins 43 A and 43 B.
  • the damper seal 22 c is fixed to an inner peripheral surface 22 bi of the split ring 22 b .
  • a member having a honeycomb structure and opening on a radial inner side Dri or the like can be used as the damper seal 22 c.
  • the damper seal 22 c exemplified in this embodiment has the two inner peripheral surfaces 22 ca and 22 cb facing the respective tips 43 a of the fins 43 A and 43 B. These inner peripheral surfaces 22 ca and 22 cb constitute the inner peripheral surface of the turbine casing 22 at the location where the damper seal 22 c is disposed. In other words, the gap between the inner peripheral surface 22 ca of the damper seal 22 c and the fin 43 A and the gap between the inner peripheral surface 22 cb and the fin 43 are the same clearance C 1 .
  • the inner peripheral surfaces 22 ca and 22 cb of the damper seal 22 c in this embodiment are respectively formed in parallel with the axis Am and have different positions in the radial direction Dr.
  • the damper seal 22 c is formed in a step shape.
  • the shape of the damper seal 22 c is not limited to the shape exemplified in this embodiment.
  • the tips 43 a of the fins 43 A and 43 B may be disposed so as to face the inner peripheral surface 22 bi of the split ring 22 b with the damper seal 22 c omitted in the turbine casing 22 .
  • the turbine stationary blade 26 includes at least a stationary blade shroud 51 and a stationary blade main body 52 .
  • the stationary blade shroud 51 forms a cavity Ct with the rotor blade shroud 42 and the fin 43 B.
  • the stationary blade shroud 51 is disposed downstream of the turbine rotor blade 24 in the direction in which the main flow M flows (hereinafter, simply referred to as the downstream side) and fixed to the turbine casing 22 .
  • the stationary blade shroud 51 in this embodiment includes a hook portion 51 a on the upstream side in the direction in which the main flow M flows (hereinafter, simply referred to as the upstream side).
  • the stationary blade shroud 51 is fixed to a downstream-side end part 22 ba of the split ring 22 b by the hook portion 51 a .
  • the stationary blade shroud 51 is formed in an annular shape continuous in the circumferential direction Dc about the axis Am.
  • the flow path of the main flow M is formed on the radial inner side Dri of the stationary blade shroud 51 .
  • the stationary blade main body 52 extends from the stationary blade shroud 51 toward the radial inner side Dri.
  • the turbine stationary blade 26 is fixed to the turbine casing 22 via the stationary blade shroud 51 .
  • the turbine 3 described above further includes a guide member 53 in the cavity Ct.
  • the guide member 53 extends from the radial outer side Dro toward the radial inner side Dri.
  • the guide member 53 is formed in an annular shape continuous in the circumferential direction Dc.
  • the guide member 53 may be integrally molded and form an annular shape as in the case of the rotor blade shroud 42 or may form an annular shape by a plurality of segments (that is, arc-shaped members) being combined.
  • An inner-side end part 53 a that is on the radial inner side Dri of the guide member 53 faces the outer peripheral surface 42 a of the rotor blade shroud 42 via a gap.
  • the inner-side end part 53 a of the guide member 53 is disposed so as to face a downstream-side end part 42 at in the radial direction Dr.
  • the downstream-side end part 42 at is the part of the outer peripheral surface 42 a of the rotor blade shroud 42 that is positioned on the most downstream side.
  • the inner-side end part 53 a in this embodiment has a surface parallel with the downstream-side end part 42 at.
  • a clearance C 2 of the gap formed between the inner-side end part 53 a and the downstream-side end part 42 at is formed so as to be larger than the clearance C 1 described above and is formed so as to be smaller than a distance C 3 between an inner peripheral surface 51 b of the stationary blade shroud 51 and the outer peripheral surface 42 a of the rotor blade shroud 42 in the radial direction Dr.
  • the inner-side end part 53 a of the guide member 53 is disposed closer to the radial inner side Dri than the inner peripheral surface 51 b of the stationary blade shroud 51 .
  • FIG. 2 illustrates a case where the inner-side end part 53 a is formed in parallel with the downstream-side end part 42 at . However, it is also possible that the inner-side end part 53 a does not have a surface parallel with the downstream-side end part 42 at.
  • the downstream-side end part 42 at of the rotor blade shroud 42 extends in parallel with the axis Am.
  • the rotor blade shroud 42 in this embodiment is inclined with respect to the axis Am so as to be separated to the radial outer side Dro and the downstream side.
  • the part where the downstream-side end part 42 at of the rotor blade shroud 42 is formed has a thickness in the radial direction Dr that gradually decreases toward the downstream side in the axial direction Da. It should be noted that a case where the downstream-side end part 42 at is formed in the rotor blade shroud 42 illustrated in FIG. 2 is sharp toward the downstream side in the axial direction Da has been exemplified and the part does not necessarily have to be sharp.
  • the guide member 53 includes an inclined portion 54 .
  • the inclined portion 54 is inclined so as to approach the turbine stationary blade 26 in the axial direction Da, that is, downstream from the inner-side end part 53 a toward the radial outer side Dro.
  • an outer-side end part 53 b which is the end part of the guide member 53 that is on the radial outer side Dro, is fixed to an upstream-side end part 51 c of the stationary blade shroud 51 .
  • the inclination angle of the inclined portion 54 is an inclination angle corresponding to the positional relationship between the upstream-side end part 51 c of the stationary blade shroud 51 and the downstream-side end part 42 at of the rotor blade shroud 42 .
  • FIG. 2 illustrates a case where the inclination angle of the inclined portion 54 is constant and the inclination angle of the inclined portion 54 may not be constant.
  • the shape of the outer-side end part 53 b of the guide member 53 is not limited to the shape illustrated in FIG. 2 .
  • the shape of the outer-side end part 53 b may be appropriately changed in accordance with the shape of the location where the outer-side end part 53 b is fixed.
  • the gas turbine 100 of this embodiment has the configuration described above. Next, the action of the gas turbine 100 will be described with reference to FIG. 2 .
  • a part of the main flow M of the combustion gas G flows into the cavity Ct by passing through the clearance C 1 of the fins 43 A and 43 B.
  • a combustion gas G 1 that has flowed into the cavity Ct flows along the inner peripheral surface 22 cb of the damper seal 22 c .
  • the flow of the combustion gas G 1 is guided toward the radial inner side Dri by the guide member 53 .
  • a combustion gas G 2 that flows out of the cavity Ct flows in the axial direction Da through the gap between the guide member 53 and the downstream-side end part 42 at .
  • the combustion gas G 2 flowing out of the cavity Ct is contracted by the combustion gas G 1 guided toward the radial inner side Dri by the guide member 53 and the flow rate thereof is reduced.
  • the pressure of the contracted combustion gas G 2 is recovered by the contracted combustion gas G 2 passing through the gap of the clearance C 2 , which is larger than the clearance C 1 .
  • the flow speed of the combustion gas G is reduced before the combustion gas G merges with the main flow M.
  • the combustion gas G 2 merges with the main flow M after being blown out downstream along the axis Am from the cavity Ct.
  • the combustion gas G 1 that has passed between the damper seal 22 c and the fin 43 B flows into the cavity Ct formed by the rotor blade shroud 42 , the fin 43 B, and the stationary blade shroud 51 . Then, the combustion gas G 1 that has flowed into the cavity Ct passes as the combustion gas G 2 between the inner-side end part 53 a of the guide member 53 and the outer peripheral surface 42 a of the rotor blade shroud 42 , which are spaced apart in the radial direction Dr. Accordingly, the combustion gas G 2 is blown out in the axial direction Da from the cavity Ct.
  • the flow of the combustion gas G 1 that has passed between the damper seal 22 c and the fin 43 B and flowed into the cavity Ct can be guided to the radial inner side Dri by the guide member 53 . Accordingly, it is possible to cause the combustion gas G 1 to collide with the combustion gas G 2 , which is about to flow into the gap between the inner-side end part 53 a of the guide member 53 and the outer peripheral surface 42 a of the rotor blade shroud 42 , from a direction intersecting with the flow of the combustion gas G 2 .
  • the flow of the combustion gas G 2 about to flow into the gap between the inner-side end part 53 a of the guide member 53 and the outer peripheral surface 42 a of the rotor blade shroud 42 can be contracted and the flow rate of the cavity flow, which is the combustion gas G 2 that is blown out of the cavity Ct, can be reduced.
  • the mixing loss at a time when the cavity flow collides and is mixed with the flow of the main flow M that has passed through the turbine rotor blade 24 can be reduced and the output of the gas turbine 100 can be improved.
  • downstream-side end part 42 at of the outer peripheral surface 42 a of the rotor blade shroud 42 facing the inner-side end part 53 a is formed in parallel with the axis Am.
  • contact between the guide member 53 and the rotor blade shroud 42 can be prevented in a case where the rotor blade shroud 42 is displaced in the axial direction Da with respect to the guide member 53 .
  • the guide member 53 includes the inclined portion 54 in the embodiment described above, and thus the flow of the combustion gas G 2 about to flow in between the inner-side end part 53 a of the guide member 53 and the outer peripheral surface 42 a of the rotor blade shroud 42 can be further contracted.
  • the clearance C 2 is larger than the clearance C 1 , the cross-sectional area of the flow path formed between the inner-side end part 53 a and the outer peripheral surface 42 a of the rotor blade shroud 42 can be increased. Accordingly, it is possible to reduce the flow speed of the combustion gas G 2 flowing through the gap between the inner-side end part 53 a and the outer peripheral surface 42 a of the rotor blade shroud 42 . As a result, it is possible to further prevent the flow of the main flow M from being affected.
  • the inner-side end part 53 a of the guide member 53 is disposed closer to the radial inner side Dri than the inner peripheral surface 51 b of the stationary blade shroud 51 . Accordingly, it is possible to prevent the cavity flow blown out of the cavity Ct from colliding with the stationary blade shroud 51 . Accordingly, it is possible to prevent the cavity flow from colliding with the stationary blade shroud 51 , changing in direction, and merging with the main flow M from a direction intersecting with the main flow M.
  • FIG. 3 is a partial cross-sectional view corresponding to FIG. 2 in each modification example of the embodiment of the present invention.
  • the fixing position of the guide member 53 is not limited to the stationary blade shroud 51 .
  • the guide member 53 may be fixed to the inner peripheral surface 22 bi of the split ring 22 b as in a guide member 153 , which is indicated by a solid line in FIG. 3 .
  • the fixing position of a guide member 253 may be a downstream-side surface 22 d of the damper seal 22 c.
  • the effect of contracting the combustion gas G 2 flowing out of the cavity Ct can be obtained and the flow speed of the combustion gas G 2 flowing out of the cavity Ct can be reduced. Accordingly, the mixing loss at a time when the cavity flow collides and is mixed with the flow of the main flow M can be reduced. Accordingly, the output of the gas turbine 100 can be improved.
  • the present invention is not limited to the configuration of the above embodiment or each modification example and a change in design is possible within the gist thereof.
  • downstream-side end part 42 at of the outer peripheral surface 42 a of the rotor blade shroud 42 is formed in parallel with the axis Am.
  • the downstream-side end part 42 at is not limited to the formation parallel with the axis Am.
  • the guide member 53 includes the inclined portion 54
  • the guide member 153 includes an inclined portion 154
  • the guide member 253 includes an inclined portion 254
  • the inclined portions 54 , 154 , and 254 may not be provided.
  • the guide member 53 may be formed so as to extend in, for example, the radial direction Dr.
  • the clearance C 2 may be the same as or slightly smaller than the clearance C 1 .
  • a single-shaft turbojet engine has been described as an example of the aircraft gas turbine in the embodiment described above.
  • the present invention is also applicable to a multi-shaft turbofan engine, a turboshaft engine for helicopters, and the like.
  • the compressor 1 is not limited to the axial compressor.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
US16/761,510 2017-12-28 2018-12-04 Aircraft gas turbine, and rotor blade of aircraft gas turbine Active 2038-12-25 US11339676B2 (en)

Applications Claiming Priority (4)

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JPJP2017-253224 2017-12-28
JP2017-253224 2017-12-28
JP2017253224A JP7086595B2 (ja) 2017-12-28 2017-12-28 航空機用ガスタービン
PCT/JP2018/044544 WO2019131011A1 (ja) 2017-12-28 2018-12-04 航空機用ガスタービン及び航空機用ガスタービンの動翼

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US11339676B2 true US11339676B2 (en) 2022-05-24

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Publication number Priority date Publication date Assignee Title
EP3822461A1 (en) * 2019-11-15 2021-05-19 MTU Aero Engines AG Axial turbomachine sealing system
JP6808872B1 (ja) 2020-04-28 2021-01-06 三菱パワー株式会社 シール装置及び回転機械
FR3120895B1 (fr) * 2021-03-16 2024-07-12 Safran Aircraft Engines Dispositif de joint d’etancheite a labyrinthe

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Also Published As

Publication number Publication date
CA3080462C (en) 2022-06-21
WO2019131011A1 (ja) 2019-07-04
US20210180464A1 (en) 2021-06-17
CA3080462A1 (en) 2019-07-04
EP3734020B1 (en) 2023-03-22
JP7086595B2 (ja) 2022-06-20
JP2019120140A (ja) 2019-07-22
EP3734020A4 (en) 2020-12-16
EP3734020A1 (en) 2020-11-04

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